Accordion, folding and cutting apparatus

ABSTRACT

Apparatus for forming accordion folds in a longitudinally traveling web of substantially uniform width and indefinite length including web cutting means disposed upstream or downstream of said folding apparatus.

United States Patent 1191 De Ligt 1451 Sept. 9, 1975 ACCORDION, FOLDINGAND CUTTING [56] References Cited APPARATUS UNITED STATES PATENTS [75]Inventor: John De Ligt, Covington, Va. 1,109,296 9/1914 Lewis 270/732,775,934 1/1957 Luehrs 271/206 [731 Assgneei l i Cmlmamn, New York3,391,928 7/1968 Mowry 271/204 [22] Fil d; J l 12, 1973 PrimaryExaminerMelvin D. Rein Assistant ExaminerA. J. Heinz [21] Appl' 378600Attorney, Agent, or Firm-W. Allen Marcontell;

Related US. Application Data RiChard L- ChmalZ [62] Division of Ser. No.176,487, Aug. 31, 1971, Pat. No.

3,784,188. [57] ABSTRACT Apparatus for forming accordion folds in alongitudi- [52] US. Cl. 270/61 F; 226/173 Dally traveling Web fsubstantially uniform width and [51] Int. Cl. B65H 45/00 indefinitelength including web cutting means disposed [58] Field Of Search 270/79,73; 34/162;

upstream or downstream of said folding apparatus.

4 Claims, 13 Drawing Figures IPATENTEDSEP 197s SHEET 1 [IF 5 PATENTEDSEP 9 I975 SHEET 2 [1F 5 ACCORDION, FOLDING AND CUTTING APPARATUS CROSSREFERENCE TO RELATED APPLICATION The present application is a divisionof my earlier application Ser. No. 176,487 filed Aug. 31, 1971 and nowissued as U.S. Pat. No. 3,784,188.

BACKGROUND OF THE INVENTION 1. Field of the Invention The presentinvention relates to the field of paper converting and comprisesapparatus for accordion folding and cutting of a continuous paper websupply.

2. Description of the Prior Art The continuous, mechanized, accordionfolding of a paper web of indefinite length has long been a valuabletechnique in the process of converting large roll quantities of paperinto smaller, more convenient units suitable for individual consumerhandling. Through the years, many devices to perform this function haveevolved as the demand for greater web speed has in creased.

Among such prior art devices have been the inventions of Meisel, U.S.Pat. No. 568,307, and Teall, U.S. Pat. No. 1,290,800. Both of theseinventions, like that of the present, utilize identical link chaincarriers on opposite sides of an oncoming web having a multiplicity ofprojections secured with uniform spacing around the periphery of eachchain set which operatively cooperate to displace the web first to oneside of a center plane and then to the other, forming a small radiuscrease at the position of direction reversal. However, both of saidearlier inventions require substantial dynamic mass as related to thefold length: an intolerable characteristic for high speed machinery.

Moreover, due to the large turning radius of such prior art machines,similarly large clearancesfrom the point of crease formation to othercooperating machinery such as web cutters are required. An undesirableincident of such large clearances is the long, uncontrolled paper tailfollowing a prefold web cut which must be caught and drawn into theaccordion fold machinery to a point of positive control.

The present invention discloses a continuous web, accordion foldingapparatus suitable for construction with small, light weight elementscommensurate with high speed operation.

Another object of the present invention is to provide accordion foldingapparatus requiring small operational clearance to decrease theproximity between a pre-creasing web cutter and the first point ofpositive control within the folding apparatus.

Other objects of the present invention include the disclosure of apost-creasing web cutting apparatus for severing a continuous web in thebight of a crease after the formation of same.

SUMMARY OF THE INVENTION The folding apparatus of the present inventioncomprises two identical pairs of link-chain circuits, each pair beingdisposed on opposite face sides of an oncoming web of paper or otherthin sheet material of indefinite length. Chain circuits respective toeach pair are disposed for running in parallel planes around respectivesprocket sets. Each chain in a pair has secured thereto the respectivelyopposite ends of several tucker and gripper bars extending between andacross the two chains of a pair. Said tucker and gripper bars arepositioned perpendicularly to the chain running plane and distributedalternately at uniform intervals around the circuit periphery.

Each gripper bar comprises two, channel shaped structural members, eachhaving one leg thereof secured to one of two longitudinally contiguouschain links. The bight openings of said channels are disposed in facingopposition and filled with a soft, compliant substance such aselastomer.

Each tucker bar comprises a structural T element having the crossmemberthereof secured to respective chain links and the T leg projectingperpendicularly therefrom.

operationally, the two chain pairs are synchronized whereby the tuckerbar on one chain pair coincides with the gripper bar nip opening of theother chain pair. As the two, longitudinally contiguous links retainingthe gripper bar are turned over a small diameter sprocket, theconsequent angular divergence between the gripper faces causes a nip toopen therebetween. Said nip opening receives the tucker bar leg as itrolls a projection of the web into meshing contact with the nip opening.Separation from the sprocket returns the two contiguous gripper barcarrier links to a straight line geometry thereby closing the gripperfaces on the web held therebetween.

Since the straight-run sections of chain circuit departing from themeshing sprockets are aligned for slight relative divergence, the tuckerleg is withdrawn from the gripper nip at very slight planarmisalignment. As soon, however, as the tucker leg is withdrawn from thegripper, the chain angle of divergence is increased greatly by turningaround an idler sprocket having a chain engagement profile such as toretain a straight line geometry between the two contiguous gripper barcarrier links. This geometry prevents the gripper from opening andprematurely releasing the crease.

This increased divergence angle rapidly advances the web crease to thedesired release position where at the chain circuit is directed aroundanother, small diameter, conventional profile, sprocket for the purposeof opening the gripper to release the web.

If the web is to be cut following folding, a reciprocating blade engagesthe web along the crease bight. Simultaneously, a set of chain driven,cylindrical rollers are positioned against the web on the side oppositefrom the blade edge for loaded rolling contact there along to cut theweb.

As an alternative embodiment of the invention, an interleaved series ofshort sheets may be accordion folded into a rectangular dispensing stackby prefold cutting the webs of two, independent supply streams intosheet length increments, merging the two supply streams into one, doublelayer stream with the transverse edges of one stream indexed to coincidewith the midpoint between sheet edges of the other stream and orientingthe double layer stream with the present folding apparatus to grasp,within the nip of a single gripper, two, serially adjacent, transversesheet edges within the linking bight of a laterally adjacent sheetcrease.

BRIEF DESCRIPTION OF THE DRAWINGS Relative to the drawings wherein likereference characters designate like or corresponding parts throughoutthe several views;

FIG. 1 is a line schematic of the accordion folding apparatus of thepresent invention integrated with a postfold cutting apparatus;

FIG. 2 is a partial elevational view of the folding apparatus of FIG. 1as seen at out II-II;

FIG. 3 is a detail of the chain carried tucker and gripper elements ofthe folding apparatus;

FIG. 4 is a schematic illustrating the mechanics operative in placing atransversely creased portion of web within the open nip of a gripperelement;

FIG. 5 is a geometric detail of the cam element for turning the foldingapparatus chain direction without prematurely opening the grippers;

FIG. 6 is a plan detail of the rolling cutter apparatus for cutting aweb after the accordion fold is formed;

FIG. 7 is an isometric schematic showing the power transmission train tothe rolling-cutter apparatus;

FIG. 8 is a plan view of an alternative scheme for selectivelyretracting the rolling cutters from the reciprocating blade table plane;

FIG. 9 is a sectional elevation of FIG. 8 as seen across cut IXIX;

FIG. 10 is a second alternate to the rolling-cutter apparatus of theinvention;

FIG. 11 is an exaggerated schematic of folded product from the apparatusillustrated in FIG. 12;

FIG. 12 is a folding apparatus of the present invention integrated witha prefold-cutting apparatus for producing the interleaved sheet productof FIG. 11.

FIG. 13 is a schematic of an alternative blade shape and associate webcutting pattern available from the roller-cutter apparatus of thepresent invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT 1. Operation Flow SequenceStarting with the FIG. 1 schematic, a paper web W of indefinite lengthis shown as delivered to the accordion folding apparatus at a controlledrate by pulling rolls 20. Right and left roller chain circuits 3a and 3bfunctionally cooperate in the proximal region A to alternately engagethe web W at regularly spaced distances along the web length. Theengagement forms a straight crease or pinch line extendingperpendicularly transverse to the web length axis with the bightopenings of successive creases facing in alternately oppositedirections, i.e. away from the chain supporting that particular crease.

Each crease is carried by its respective supportive chain to the lower,release proximity B where the web panel W is substantially horizontaland will gravity drop to a flat position without wrinkling.

Although this disclosure of the preferred embodiment describes theendless carrier elements 3a and 3b as roller chains, it should beappreciated that numerous alternatives, generically characterized asendless traction means, may be equally suitable for particularapplications. Among such alternative may be included other types ofchain drives, belts, ropes or cables. Relative rotational timing betweenthe two circuits 3a and 3b is critical since rigid elements structurallysecured to each circuit must physically cooperate by meshing. However,it is entirely possible to design a belt carrier system in which theinherent slippage between the traction carriers and the associatesheaves (sprockets) is not so great as to be within meshing tolerancefrom one meshing half cycle to the next. Coincident therewith,

each incident of meshing would physically correct any misalignment ofrelative index occurring within the preceding half cycle of operation.

To cut the infinite length web W uniform lengths terminating preciselyalong a crease bight centerline, a post-fold cutting mechanism 4 isdisposed between the folding apparatus and product receiving hopper 9.If provision for cutting web creases falling on either side of web flowcenterline C is desired, cutting mechanism 4 may comprise two bladetables 41a and 41b and two roller-cutting units 42a and 42b. Blade table41a and roller unit 42a functionally cooperate as a set to sever creaselines on the right side of centerline C whereas table 41b and rollerunit 42b cooperate for left side cuts, exclusively.

An alternative embodiment is illustrated by FIG. 12 where prefoldcutting is performed on two web sources 10 and 11 for the purpose ofinterleaving one panel section of a folded sheet between integral panelsof a second, folded sheet.

2. Folding Mechanism Each chain circuit 3a and 3b in FIG. 1 comprises apair of roller chains 30 encompassing sprockets 31, 32, 33 and cam 34.There being two, parallel, chain running planes, R and L (FIG. 2),having rigid transverse structural ties (tucker 35 and gripper 36), ineach chain circuit 3a and 3b, a total four chain closures, L30a, R3011,L301) and R30b, are described herein. It should be understood, however,that the number of running planes, e.g. R and L, may be increased forthe purpose of folding wider paper. To do so, would increase the numberof chain closures by two for each running plane added.

Both chain circuits 3a and 3b being of identical construction, furtherdescription will be focused on circuit 3a.

Relative to FIGS. 2 and 3, it may be seen that each gripper bar 36comprises two, longitudinal structural channel elements 61 filled withelastomer 62. The interface between the two elastomer portions 62 isseparable to form respective gripper jaws 66. The two elements 61 ofeach gripper bar 36 are respectively carried by the two, relativelyarticulatable, contiguous, link pairs 630 and 631' forming link set 64.Tabs 65, integral with the links 63, may be used as attachment platformsfor the channels 61 to the links 63.

Tucker bar 35 is shown to be a unitary, extruded T or L elementcomprising cross-bar 51 and leg projection 52. Like the gripper 36,tucker bar 35 may be secured to link pair 53 by means of an attachmentplatform 55.

The number of tuckers 35 and grippers 36 allowed on each chain circuitis arbitrary above the permissible minimum of '2 tuckers and 2 grippers.For purposes of timing, coordination, etc., there should be a wholenumber ratio between the sum of grippers and tuckers and the length ofthe circuit in pitches.

The distance D between a gripper 36 and adjacent tuckers 35 on the samechain is related to, but not the same as, a panel length S. Therefore,the linear quantity of web W pushed by the rolls 20 between chaincircuits 3a and 3b in the interim between points of tuckergripperengagement is greater than the distance D as represented by the sag inFIG. 1 web sections W and W The opening and closing operations ofgrippers 36 are functions of relative geometry as the chains are drawnover the periphery of sprockets'3l and 32. The distance P(FIGS. 3 and 5)between chain rollers 37 is held constant by the interconnecting rigidlinks 63. Accordingly, the sprocket pitch P may be defined as a chordsubtending an a degree arc on the pitch circle M of radius of N (FIG.4). Gripper faces 66 are placed at a distance K (FIG. 3) above the planeincluding the axes of two adjacent rollers 37 and disposed to abut, ornearly so, between sprockets when the roller center beneath the gripperface 66 falls into a plane common to the centers of those rollersadjacent both sides. Since the geometry of a link pair 63 betweenadjacent rollers 37 is rigid, when a gripper bar unit 36, havingcooperative jaw elements on two adjacent link pairs 631' and 630 of alink set 64, is drawn over the periphery of a sprocket, the jaws 66 areseparated by a mean distance substantially equal to 2(K) (Sin a). As thechain departs from contact with a sprocket, the roller centers return tothe straight line relationship thereby closing the jaws 66.

Rotational timing of the chain circuits 3a and 3b is as shown by FIGS. 1and 4 whereby the tucker leg 52 of one chain circuit rolls between theopened jaws 66 of gripper 36 on the opposite chain circuit. Since themeshing of cooperative tuckers and grippers is from opposite sides ofthe web W, a portion thereof is pressed between the open gripper jaws 66as shown in FIG. 4. As the chain rolls off the sprocket 31b, jaws 66 arepulled together to close on tucker leg 52, clamping the web Wtherebetween.

In order to withdraw the tucker leg 52 from the nip of jaws 66 withoutdisrupting or damaging the web therebetween, the chains course halfangle of departure a from sprockets 31a and 31b must be held to shallowmaximums. The exact angle may be analytically derived by those ofordinary skill in the art but for purposes of example, half angle a maybe in the order of 5.

At this point in the operation, gripper 36 has estalished a crease inthe web and leg 52 of tucker 35 has been withdrawn therefrom. Moreover,the crease held by chain circuit 3b is slightly to the left (FIG. 1) ofcenter plane C. The next succeeding crease will be held by chain circuit3a and will be drawn to the right of center plane C thereby establishingan accordion geometry bias. However, no reliably repetitive fall patternmay be acquired or positive control exercised if the web is released.Wrinkles and irregular stacking patterns will result if the web isreleased from the positions W or W Therefore, the generally verticaldisposition of the accordion must be reoriented to a generallyhorizontal disposition as represented by web sections W and W Toaccomplish this result, the creased end of web section W held by chaincircuit 3b must be advanced laterally (to the left) from the centerplane C at a greater rate than the circuit 3a held crease of the samesection W Simultaneously, the vertical displacement between the two endsof section W must be reduced.

An obvious technique of such reorientation is to increase the rate ofcircuit divergence by the half angle quantity of B, 25 for example, asby bending around an intermediate cam 34. But if the idler includes aconventional profile, gripper jaws 66 will open and release the webprematurely as the gripper bar 36 passes thereover.

To avoid this result, cam 34 of the present invention are provided withnotches 38 which are rotationally timed to receive the center roller ofthe three roller groups supporting a gripper bar link set 64. Asrepresented by FIG. 5 the centers of the three link set 64 supportiverollers 37 are allowed to sustain a straight line relationship at thepoint of chain tangency to the idler 34. The depth and profile of thenotch 38 may be determined analytically by those of ordinary skill inthe art from chain pitch P, chain roller radius r, the initial departureangle a and the final departure angle ,8. Since link pairs 631' and 630are precluded from relative angular displacement as the set 64 turnsabout idler 34, jaws 66 are held tightly closed on the crease of web W.

The next critical design point of the present invention is the verticalplacement of release sprocket 32 below idler 34. The controllingcriterion is the length of a moderately tensioned web secton W so thatgripper bar 36 on chain circuit 3b will open as the gripper 36 on chaincircuit 3a moves into position to pull the 3b circuit crease frombetween jaws 66.

If only continuous and rapid accordion folding of web W is desired, theaforedescribed apparatus will flawlessly deliver a rectangular columncontinuum of accordion folded web to a receiving station such as chuteor hopper 9.

However, if finite lengths of folded web, in whole number increments ofweb sections between creases, are desired, the aforedescribed foldingapparatus may have integrated therewith the post-fold cutting mechanism4.

3. Post-Fold Cutting Mechanism The preferred embodiment of the post-foldcutter comprises two blade tables 41a and 41b disposed in the same planebelow release sprockets 32.

The two tables 41a and 41b function alternately with one, 41a of FIG. 1,penetrating the material flow column between web sections W and W fromthe left of center plane C and the other, 41b, penetrating between websections W and W from the right of center plane C.

Both tables 41a and 41b are provided with knife edges 43a and 43b forpositionment within the bight of a crease.

Rotating into position against the knife edges 43a and 43b but fromopposite sides of the web W are respective roller mechanisms 42a and42b. As best illustrated by FIG. 6 relatively wide, flat tread wheels 44cut the web W by pressing same against the knife edge 32a with rollingcontact. Resiliently loaded backing bar 45 maintains a relativelyconstant contact pressure between wheels 44 and the web W to assurecomplete cutting across the full web width as the edge and treadsurfaces wear. The treads of wheels 44 should be flat, i.e. relativelylong surface elements of a regular cylinder, to provide broadaccommodation for the degree of functional misalignment as eventually,if not initially, occurs in high speed, cyclically reversing machinery.

Rollers 44 are mounted on carrier links 47 of a sprocket driven rollerchain 46. Spacing between rollers 44 along the chain 46 may be asdesired, one factor of consideration being the length of allowablecutting interim within an operational cycle: a smaller separationdistance between rollers yields a shorter cutting time for a given chainspeed.

It should be appreciated that a cutting operation performed by theaforedescribed apparatus of this invention is not only rapid due tosimultaneous cutting of several small increments across the web widthbut is also neat, there being no opportunity for shredding due to blademisalignment. The present invention allows only one cut line, thatallowed by the continuous line of knife edge 43a or 43b, regardless ofthe variance the edge line may follow from true (within the limits ofthe wheel 44 tread width). Therefore, a single, continuous cut line maybe achieved with the rapidity of multiple cutters.

Although any number of mechanisms may be devised for selectivelyengaging the knife edges 43 with rollers 44, the schematic shown inisometric by FIG. 7 is of a particularly SUCCSSfill example. Knifetables 41a and 41b are mounted on guide bars 70 and reciprocably drivenby four-bar crank mechanisms 71a and 71b. Since the web cuttingoperation is cyclical over an interrrupted period, greatest flexibilityfor programing the cycle period is afforded by linking the input powerline shaft 72 with the lateral, power transfer shafts 75a 'and 75bcarrying lateral spur gears 73a and 73b through electrically latched,single revolution clutches 74a and 74b such as a Type 6 as specified bythe Hilliard Corporation of Elmira, New York.

Condition sensory means such as a limit switch or photo sensory switch,not shown, for actuating either of clutches 73a or 73b by the emissionof a suitable elec trical signal, may be responsive to select portionsof the folding mechanism or drive therefor such as the notched can 34.

With each operational cycle of the blade tables 41a and 41b, so too, arepositioned roller-cutter units 42a and 42b by means of carriage 48,parallel swing arms 49 and eccentric 77 driven connecting rod 76.

With clutch 74a engaged, for example, power is transferred from shaft 72to shaft 75a via spur gear 730. Shaft 75a transfers power to thefour-bar linkage 71a via chain transmission 78a (thereby sliding bladetable 41a between web panels W and W (FIG. 1)). Simultaneously, chaintransmission 79a draws power from shaft 75a to rotate eccentric 77a forraising the rollercutter unit 42a into operative engagement with knifeedge 43a mounted on blade table 41a.

Roller chain 46 carrying cutting wheels 44 is driven continuously bydirect power take-off 80a from main input power shaft 72 thereby furtherminimizing the cutting delay time.

As of the aforedescribed point of operation, the cutting cycle for thecrease joined web panels W and W is only half complete although the webis completely severed. However, since the ratio between the power.

shaft 72 gear is 2:1 for a complete cycle, the one revolution clutch 74amust be actuated a second time to withdraw blade table 41a from the webflow column. This second actuation may be keyed to such an event as thecompletion of a dump cycle for hopper 9 to remove the material collectedtherein and severed from the web W by the rolling-cutter apparatus.

After the cutting plane between guide bars 70 has been cleared by theretraction of roller-cutter 42a and blade table 41a therefrom, thecircuit for actuating cutting apparatus 411) and 42b is prepared forcompletion by a second panel counting circuit. In this manner, webcreases on sequentially opposite sides of the material flow axis C arecut with a predetermined number of integrally connected panelstherebetween.

It should be understood that the scale and disposition of elements inFIG. 7 is distorted to further the ends of clarity and disclosure.Although the gear and sprocket ratios of the FIG. 7 mechanism arecritical, they are so fora very limited product range. These are matterswithin the competence of ordinarily skilled practitioners of the art andneed no further elaboration.

It should be noted, however, that depending on associated machinegeometry and the nature of power available, the rolling-cuttermechanisms disclosed by FIGS. 8, 9 and 10 may be more suitable.

The FIG. 8 and 9 embodiment, for example provides an alternative tophysically displacing a driven sprocket under load as required the FIG.7 mechanism. In FIGS. 8 and 9 the rolling contact surfaces are frustumsof regular cones 81 carried on an expansible chain circuit 82 loadedtensionally by reciprocable load shoes 83a and 8311. Linking piston rods84 fitted through cylinder block 85 rigidly unitize shoes 83a and 83bwhereby fluid pressure resiliently biased against an annular collarpiston surface (not shown) within the cylinder block 85 engages therolling contact surface 81 with the knife edge 43a. When the cut iscomplete, fluid pressure bias on the piston collar is reversed toretract all chains and roller elements from the blade tablereciprocation plane.

The rolling cutter mechanism of FIG. 10 is highly simplified andrepresents the basic elements of an application where the mostconvenient power application is a single or double stroke lineardisplacement of a machine element from point Y to point Z.'The elementsof FIG. 10 include the arcuate segment of a cylinder having a radius E.The cylindrical surface 86 is rolled into contact with the knife edge43a by driving a rod or roller element 87 along arcuate slot 88 frompoint Y to point Z. As surface 86 rolls about the axis F, the axisposition translates to point P.

FIG. 13 further illustrates the design flexibility available to thepresent invention by allowing complex cutting patterns such as theundulating or scalloped edge of panel W without sacrifice of cuttingspeed or precision. Since the thread width of rollers 37 exceeds theamplitude of knife edge 43c undulations, the cut line for web W willfollow exactly that of the knife edge notwithstanding the fact thatseveral rollers 37, rapidly traversing short increments of the webwidth, serve as separate anvils over respective increments.

Many variations of the scalloped edge scheme of FIG. 13 may becomprehended within the teaching of the invention, such as Greek scrollor sawtooth, the primary criterion being that the web W is pressedagainst all transverse elements of the edge 430 by loaded, rolling,contact pressure.

4. Prefold Cutting Mechanism Due to the relatively short radialclearance required by the sweep of tucker 35 and gripper 36 devices ofthe present invention, it is also possible to integrate the presentaccordion folding apparatus with prefold cutting apparatus to deliver acontinuum of interleaved, single folded sheets as schematicallyrepresented by FIG. 1 1. Distinctive characteristics of the FIG. 11product include sheets 23, folded so as to open to the left of thecenter line, and sheets 24, folded so as to open to the right of thecenter line. The upper panels 2314 of sheets 23 are disposed to overliethe lower panels 24L of sheets 24. Conversely, panels 2414 overliepanels 23L. integral pair of panels, 23a and 23L for example, are joinedby the bight of a crease 23b.

Relating now to the FIG. 12 apparatus for producing the product of FIG.11, there are shown two web supply streams l3 and 14 pulled from reelsand 11 by pulling rolls 15 and 16. Rotary knives 17 and 18 cut therespective webs into a continuum of sheets 23 and 24, respectively.

Subsequent to cutting, the two supply streams are merged into a singleplane of supply 21 by the converging nip 22 between belt conveyors and26. Rotation of the knife 17 is timed for 180 angular phase displacementfrom the rotation of knife 18 so that upon emergence from the nip 22,the transversely cut edges of serially adjacent sheets 23 from supplystream 13 align with the approximate midpoint between transverse edgesof laterally adjacent sheets 24. From the nip 22, the single supplystream 21 is delivered to the pickup area A between sprockets 31a and31b where the junction between serially adjacent edges of sheets 23 andthe midpoint of sheets 24 is pressed into the nip of grippers 36.

As the foregoing cycle is reversed and repeated, panels from respectivewebs are interleaved in the manner represented by FIG. 11.

Having disclosed a specific, preferred embodiment, I claim as myinvention:

1. Material transfer means comprising:

An elongated, flexible tensile element having first and second opposedfaces positioned for longitudinal movement along a relatively fixedcourse, said fixed course having at least two, non-aligned,substantially straight line adjoining segments disposed in approximatelythe same plane, each straight line segment respectively having one endthereof tangentially joining a first wheel element having a rim portiondisposed for rotation about a first axis that is substantially normal tothe plane of said straight line segments, said straight line segmentsbeing terminated at the respective other ends thereof by tangency withsecond and third rotatable wheel elements having respective rimportions, the first face of said flexible tensile element being biasedby tensile stress therewithin against said rim portions of said wheelelements toward respective axes of rotation;

A cooperative pair of gripping jaw mounting mem bers adjoining eachother, secured to and longitudinally spaced along said tensile element,each mounting member having a rigid projection extending from saidtensile element second face in a direction opposite from said axes ofrotation, gripping jaw means for cooperatively gripping an articletherebetween comprising a.jaw element secured to respective projections,each of said mounting members being rotatively secured to said tensileelement about a pair of articulation axes rigidly positioned relative tosaid projection, said articulation axes passing through said tensileelement substantially perpendicular to the plane of said straight linesegments; and

Profile means in the rim of said first wheel element being rotativelyregistered to engage at least one of said articulation axes respectiveto a cooperative pair of mounting members with a surface discontinuityfor simultaneously supporting all of said articulation axes associatedwith a cooperating pair of mounting members in a common plane that issubstantially perpendicular to the plane of said straight line segmentsas said articulation axes travel with said tensile element about saidfirst axis from one straight line segment to the other whereby saidgripping jaw means are prevented from relatively separating to releasean article therebetween while in traverse about said first axis.

2. Material transfer means as described by claim 1 wherein saidelongated tensile element is a chain of rigid links, said mountingmembers comprising adjacent links in said chain, each link beingpivotably joined to a longitudinally adjacent link by a journal havingan axis that is coaxial with one articulation axis respective to each ofsaid links.

3. Material transfer means as described by claim 2 wherein said wheelelements comprise chain sprockets having journal saddles between, eachof said journal saddles having a bight portion that is radially mostproximate of said first axis, said first wheel element discontinuitysurface comprising at least three adjacent saddle bight portions alignedwith a common chord across said first wheel element.

4. Material transfer means as described by claim 2 wherein said firstwheel element surface discontinuity comprises a notch in the rim of saidfirst wheel element of sufficient depth to receive a journal common tosaid cooperative pair of mounting members whereby the axes of threeadjacent link journals respective to said pair of mounting members,including said common journal, are mutually supported in the plane of achord to said first wheel element that is substantially perpendicular toa first wheel element radius that passes through the center of saidnotch.

1. Material transfer means comprising: An elongated, flexible tensileelement having first and second opposed faces positioned forlongitudinal movement along a relatively fixed course, said fixed coursehaving at least two, non-aligned, substantially straight line adjoiningsegments disposed in approximately the same plane, each straight linesegment respectively having one end thereof tangentially joining a firstwheel element having a rim portion disposed for rotation about a firstaxis that is substantially normal to the plane of said straight linesegments, said straight line segments being terminated at the respectiveother ends thereof by tangency with second and third rotatable wheelelements having respective rim portions, the first face of said flexibletensile element being biased by tensile stress therewithin against saidrim portions of said wheel elements toward respective axes of rotation;A cooperative pair of gripping jaw mounting members adjoining eachother, secured to and longitudinally spaced along said tensile element,each mounting member having a rigid projection extending from saidtensile element second face in a direction opposite from said axes ofrotation, gripping jaw means for cooperatively gripping an articletherebetween comprising a jaw element secured to respective projections,each of said mounting members being rotatively secured to said tensileelement about a pair of articulation axes rigidly positioned relative tosaid projection, said articulation axes passing through said tensileelement substantially perpendicular to the plane of said straight linesegments; and Profile means in the rim of said first wheel element beingrotatively registered to engage at least one of said articulation axesrespective to a cooperative pair of mounting members with a surfacediscontinuity for simultaneously supporting all of said articulationaxes associated with a cooperating pair of mounting members in a commonplane that is substantially perpendicular to the plane of said straightline segments as said articulation axes travel with said tensile elementabout said first axis from one straIght line segment to the otherwhereby said gripping jaw means are prevented from relatively separatingto release an article therebetween while in traverse about said firstaxis.
 2. Material transfer means as described by claim 1 wherein saidelongated tensile element is a chain of rigid links, said mountingmembers comprising adjacent links in said chain, each link beingpivotably joined to a longitudinally adjacent link by a journal havingan axis that is coaxial with one articulation axis respective to each ofsaid links.
 3. Material transfer means as described by claim 2 whereinsaid wheel elements comprise chain sprockets having journal saddlesbetween, each of said journal saddles having a bight portion that isradially most proximate of said first axis, said first wheel elementdiscontinuity surface comprising at least three adjacent saddle bightportions aligned with a common chord across said first wheel element. 4.Material transfer means as described by claim 2 wherein said first wheelelement surface discontinuity comprises a notch in the rim of said firstwheel element of sufficient depth to receive a journal common to saidcooperative pair of mounting members whereby the axes of three adjacentlink journals respective to said pair of mounting members, includingsaid common journal, are mutually supported in the plane of a chord tosaid first wheel element that is substantially perpendicular to a firstwheel element radius that passes through the center of said notch.